JP2012154476A - One-way clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a one-way clutch that can reliably lock without depending on the purpose of use or environmental conditions.SOLUTION: A roller clutch 10 includes: an inner ring 12; an outer ring 11 disposed to be relatively rotatable with respect to the inner ring 12; a plurality of rollers 13 disposed between an outer circumference face of the inner ring 12 and an inner circumference face of the outer ring 11; a retainer 14 retaining the rollers 13; and a plurality of first springs 15 and second springs 15', which are disposed in the retainer 14 and press the respective rollers 13 in each locking direction. Each of the second springs 15' presses each of the rollers 13 with a pressing force larger than that of each of the first springs 15.

Description

  The present invention relates to a one-way clutch that transmits power only in one direction.

  Conventionally, a roller clutch is known as this type of clutch. (For example, refer to Patent Document 1). A conventional roller clutch 100 shown in FIG. 6 includes a driven-side outer ring 101, a driving-side shaft 102 inserted concentrically inside the outer ring 101, an outer peripheral surface of the shaft 102, and an inner peripheral surface of the outer ring 101. A plurality of rollers 103 inserted between them, a holder 104 that rotatably holds the rollers 103 in the pocket 104p, and a roller 104 supported by the holder 104 to urge each roller 103 in the circumferential direction (power transmission direction) And a spring 105.

  In the roller clutch 100 described above, the outer ring 101 is formed in a cylindrical shape, and the inner peripheral surface 101n has a cam surface K whose diameter is increased in a concave shape. The cam surface K and the outer peripheral surface 102g of the shaft 102 form a wedge-shaped space W in which the roller 103 can be engaged. The wedge-shaped space W is formed so as to narrow toward the rotational power transmission direction. In the rotational power transmission state, the spring 105 presses the roller 103 toward the narrow portion of the wedge-shaped space W, so that the roller 103 is wedge-shaped. The shaft 102 and the outer ring 101 enter the space W and are integrated (locked) via the roller 103 that cannot move, and rotational torque is transmitted. On the other hand, in the state where the rotational force is interrupted, the roller 103 enters the wide portion of the wedge-shaped space W while elastically deforming the spring 105, and the integration of the outer ring 101, the shaft 102, and the roller 103 is released and can idle Run) and the rotational torque is cut off.

JP 2001-116066 A

  One-way clutches are used in various applications such as automotive auxiliary machines, office machines, fishing tackle reels, and the like. When the one-way clutch is used, for example, in an automobile accessory, the lock and overrun may be switched at high speed. In addition, when the one-way clutch is used for a paper feeder or a fishing tackle reel of an office machine, it may be exposed to a large vibration, and when used for a fishing tackle reel, the grease viscosity is low in a low temperature environment. It can be expensive. In such a case, if the force with which the spring presses the roller toward the narrow part of the wedge-shaped space W is weak, the one-way clutch is difficult to lock.

  This invention is made | formed in view of the said situation, and is providing the one-way clutch which can be locked reliably irrespective of a use or environmental conditions.

The above object of the present invention can be achieved by the following constitution.
(1) an inner member;
An outer member arranged to be rotatable relative to the inner member;
A plurality of engagement elements disposed between an outer peripheral surface of the inner member and an inner peripheral surface of the outer member;
A cage for holding the plurality of engagement elements;
A one-way clutch comprising a plurality of elastic bodies provided in the retainer and pressing each of the plurality of engagement elements in a locking direction;
The one-way clutch, wherein at least one elastic body among the plurality of elastic bodies presses the engaging element with a larger pressing force than other elastic bodies.
(2) The one-way clutch according to (1), wherein the elastic body that presses the engaging element with a larger pressing force than the other elastic bodies has a larger amount of deflection than the other elastic bodies.
(3) The elastic body that presses the engagement element with a larger pressing force than the other elastic body is provided in the cage at a position closer to the engagement element than the other elastic body. The one-way clutch according to (2) above, wherein the amount of deflection is larger than that of the elastic body.
(4) The elastic body that presses the engaging element with a larger pressing force than the other elastic bodies is provided in a plurality at equal intervals on the circumference, (1) to (3), One term clutch.

  According to the one-way clutch of the present invention, since the engaging element pressed by the elastic body having a large pressing force is locked first, stable operation is possible regardless of the application and environmental conditions.

It is a schematic sectional drawing of the roller clutch which concerns on one Embodiment of this invention. It is a figure which shows the fixed state of the 1st spring of the roller clutch of FIG. 1, and is the figure which abbreviate | omitted the outer ring | wheel and was seen from the radial direction outer side. It is a principal part expanded sectional view which shows the fixed state of the 1st spring of the roller clutch of FIG. It is a figure which shows the fixed state of the 2nd spring of the roller clutch of FIG. 1, and is the figure which abbreviate | omitted the outer ring | wheel and was seen from the radial direction outer side. It is a principal part expanded sectional view which shows the fixed state of the 2nd spring of the roller clutch of FIG. It is a schematic sectional drawing of the roller clutch which concerns on a prior art.

  Hereinafter, an embodiment of a one-way clutch according to the present invention will be described in detail with reference to the drawings.

  As shown in FIG. 1, a one-way clutch (roller clutch) 10 according to this embodiment includes a cylindrical outer ring 11 and an inner ring that is arranged concentrically on the inner side of the outer ring 11 and rotates together with a rotating shaft (not shown). 12 and. The inner peripheral surface of the outer ring 11 is formed as a cam surface 11b having a plurality of recesses 11a formed at equal intervals in the circumferential direction. Between the cam surface 11b and a cylindrical surface 12a formed on the outer peripheral surface of the inner ring 12, a plurality of rollers 13 as engaging elements are rotatably provided. In the present embodiment, seven rollers 13 are provided.

  The roller clutch 10 includes a pair of annular rim portions 21 and 21, a pair of rim portions 21 and 21 connected in the axial direction, a plurality of column portions 22 arranged at equal intervals in the circumferential direction, The cage 14 is provided with a plurality of pockets 23 that are surrounded by two column portions 22 and a pair of rim portions 21 and 21 that are arranged in the direction and that individually accommodate the rollers 13.

  The cage 14 further includes a first spring 15 and a second spring 15 ′ that elastically press the rollers 13. In the roller clutch 10 according to this embodiment, five first springs 15 and two second springs 15 ′ are fixed to the column portion 22. The two second springs 15 'are arranged at equal intervals on the circumference, that is, at intervals of 180 °. When the inner ring 12 rotates in the torque transmission direction (clockwise direction in FIG. 1), the first spring 15 and the second spring 15 ′ cause the rollers 13 accommodated in the adjacent pockets 23 to lock in the locking direction described later. Press each one. On the contrary, when the inner ring 12 rotates in the torque non-transmission direction (counterclockwise direction in FIG. 1), the roller 13 presses the first spring 15 and the second spring 15 ′.

  2 and 3 show a state in which the first spring 15 is fixed to the column portion 22. In FIG. 2, the outer ring 11 is omitted for simplification. In the vicinity of one end in the circumferential direction of the column portion 22, a pair of end-side spring holding portions 24, 24 that are provided at both ends in the axial direction and project in the outer diameter direction are formed. Is formed with a central spring holding portion 25 protruding in the outer diameter direction. The end side spring holding parts 24, 24 and the center side spring holding part 25 are arranged in a slightly shifted state in the circumferential direction, and the first spring 15 is a circumference of the end side spring holding parts 24, 24. It is sandwiched between one side surface in the direction and the other side surface in the circumferential direction of the center side spring holding portion 25. The first spring 15 constitutes a pressing portion 15a by bending both ends thereof, and the pressing portion 15a presses the roller 13 in the locking direction d, that is, the direction in which the shallow side of the groove of the recess 11a is located. To do. The maximum amount of deflection when the first spring 15 presses the roller 13 is g.

  4 and 5 show a state in which the second spring 15 ′ is fixed to the column portion 22. In FIG. 4, the outer ring 11 is omitted for simplification. A pair of end-side spring holding portions 24 ′ and 24 ′ that are provided at both ends in the axial direction and project in the outer diameter direction are formed in the vicinity of the intermediate portion in the circumferential direction of the column portion 22. In the vicinity of the central portion, a central spring holding portion 25 ′ protruding in the outer diameter direction is formed. The end-side spring holding portion 24 ′ and the center-side spring holding portion 25 ′ are arranged with a slight shift in the circumferential direction, and the second spring 15 ′ is in the circumferential direction of the end-side spring holding portion 24 ′. It is sandwiched between one side surface and the other circumferential side surface of the center side spring holding portion 25 ′. The second spring 15 'constitutes a pressing portion 15a' by bending both ends thereof, and the roller 13 is directed by the pressing portion 15a 'in the locking direction, that is, in the direction in which the shallow side of the groove of the recess 11a is located. And press.

  Here, as shown in FIGS. 1 to 5, the pair of end portion side spring holding portions 24 ′, 24 ′ and the center side spring holding portion 25 ′ are composed of a pair of end portion side spring holding portions 24, 24 and a center side spring. It is arranged on the pillar portion 22 on the side closer to the pressing roller 13 than the holding portion 25. That is, the second spring 15 ′ is disposed closer to the roller 13 that presses each other than the first spring 15. Therefore, the maximum deflection amount G when the second spring 15 ′ presses the roller 13 is larger than the maximum deflection amount g when the first spring 15 presses the roller 13. For example, the maximum deflection amount g of the first spring 15 is 0.4 mm, while the maximum deflection amount G of the second spring 15 ′ is 0.8 mm, and the force with which the first spring 15 presses the roller is The force by which the second spring 15 ′ presses the roller is 5 gf and 10 gf.

  As described above, when the inner ring 12 rotates in the torque transmission direction by the second spring 15 ′ pressing the roller 13 with a force larger than that of the first spring 15, first, the second spring 15 ′ is locked by the second spring 15 ′. The roller 13 pressed in the direction D moves in the narrow direction of the recess 11a. As a result, the roller 13 pressed by the second spring 15 ′ is sandwiched between the cam surface 11b and the cylindrical surface 12a. Following this, the roller 13 pressed in the locking direction d by the first spring 15 is also sandwiched between the cam surface 11b and the cylindrical surface 12a to lock the cam surface 11b and the cylindrical surface 12a. Therefore, according to the roller clutch 10 of the present embodiment, it is possible to reliably lock in any environmental condition.

  On the other hand, when the inner ring 12 rotates in the torque non-transmitting direction, the roller 13 presses the first spring 15 and the second spring 15 ′, and the roller 13 moves in the wide direction of the recess 11a. Thereby, the lock of the cam surface 11b and the cylindrical surface 12a is released, and the roller clutch 10 is overrun. During the overrun of the roller clutch 10, the first spring 15 and the second spring 15 ′ are continuously pressed by the roller 13, but in the present embodiment, five of the seven springs have a small deflection amount. By using the single spring 15, friction loss can be reduced.

  Thus, according to the roller clutch 10 of the present embodiment, when the lock and overrun are switched at high speed, when exposed to large vibrations, or when the grease viscosity is high in a low temperature environment, etc. However, the second spring 15 ′ having a large force for pressing the roller 13 can be reliably locked. Further, the rotation balance of the roller clutch 10 is improved by arranging the second springs 15 ′ at equal intervals on the circumference.

  In addition, this invention is not limited to embodiment mentioned above, A change, improvement, etc. are possible suitably. For example, in the roller clutch 10 according to the above-described embodiment, the five first springs 15 and the two second springs 15 ′ are fixed to the cage 14, but the present invention is not limited to this. It is sufficient that at least one second spring 15 ′ having a large force for pressing the roller 13 is provided, or half of the total number of springs may be the second spring 15 ′. The number of second springs 15 'may be set according to the required overrun torque value. When a plurality of second springs 15 'are provided, it is preferable to provide them at equal intervals on the circumference. For example, when three second springs 15' are provided, they are 120 with respect to each other. It is preferable to arrange them at an interval of °.

  In the embodiment described above, the first spring 15 and the second spring 15 ′ are formed separately from the cage 14, but the cage and the spring may be integrally formed. For example, when the cage and the spring are integrally molded with resin, it is possible to provide a spring having a strong force for pressing the roller by increasing the thickness of at least one spring or lengthening the pressing portion.

  In the above-described embodiment, the leaf spring in which both ends are bent and the pressing portion is formed is used. However, the present invention is not limited to this, and an arbitrary spring such as a coil spring may be used.

  INDUSTRIAL APPLICABILITY The present invention can be suitably used for fishing tackle reels, paper feeding for office machines, automotive auxiliary machines, and the like.

10 Roller clutch (one-way clutch)
11 outer ring 12 inner ring 13 roller 14 cage 15 first spring 15 ′ second spring

Claims (4)

An inner member;
An outer member arranged to be rotatable relative to the inner member;
A plurality of engagement elements disposed between an outer peripheral surface of the inner member and an inner peripheral surface of the outer member;
A cage for holding the plurality of engagement elements;
A one-way clutch comprising a plurality of elastic bodies provided in the retainer and pressing each of the plurality of engagement elements in a locking direction;
The one-way clutch, wherein at least one elastic body among the plurality of elastic bodies presses the engaging element with a larger pressing force than other elastic bodies.   The one-way clutch according to claim 1, wherein an elastic body that presses the engaging element with a larger pressing force than other elastic bodies has a larger amount of deflection than the other elastic bodies.   The elastic body that presses the engagement element with a larger pressing force than the other elastic body is provided in the cage at a position closer to the engagement element than the other elastic body, so that the other elastic body The one-way clutch according to claim 2, wherein the one-way clutch has a larger amount of deflection.   The one-way clutch according to any one of claims 1 to 3, wherein a plurality of elastic bodies that press the engagement element with a pressing force larger than that of other elastic bodies are provided at equal intervals on the circumference.

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